Multi-channel heat exchanger and air conditioning refrigeration system

ABSTRACT

A multi-channel heat exchanger includes a plurality of heat exchange tubes, each heat exchange tube includes first to fourth heat exchange tube portions which are distributed along a direction from an airflow inlet side to an airflow outlet side. Each heat exchange tube portion includes at least two flow channels. The heat exchange tube has a cross section defined in a thickness direction and a width direction of the heat exchange tubes, and the cross section includes a flow section. A total area of a flow section of the first heat exchange tube portion is A1, a total area of a flow section of the fourth heat exchange tube portion is A4, and the total area A1 of the flow section of the first heat exchange tube portion is 1.05-1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion.

CROSS REFERENCES TO RELATED APPLICATION

The present application is a national phase entry under 35 USC § 371 of International Application No. PCT/CN2020/115229, filed on Sep. 15, 2020, which claims the benefit of priority to Chinese Application No. 201921648808.5, filed on Sep. 29, 2019, both of which are incorporated by reference herein in their entireties for all purposes.

FIELD

The present disclosure relates to a field of heat exchange equipment, and more particularly, to a multi-channel heat exchanger and an air conditioning refrigeration system having the same.

BACKGROUND

As an alternative technology of a copper tube fin heat exchanger, a multi-channel heat exchanger has attracted more and more attention in the field of an air conditioning technology, and has developed rapidly in recent years. Along a flow direction of a refrigerant, the refrigerant evaporates or condenses at different positions in channels arranged side by side are, thus resulting in a mismatch between a flow distribution of the refrigerant in the channels and a heat-exchange temperature difference. An obvious temperature difference occurs between a windward side and a leeward side on a section of the heat exchange tube, and an obvious overcooling or overheating temperature gradient is formed on a section of the heat exchange tube adjacent to an outlet of the heat exchanger. A temperature difference on the windward side cannot be better utilized.

SUMMARY

A multi-channel heat exchanger according to embodiments of the present disclosure includes a plurality of heat exchange tubes spaced apart along a thickness direction of the heat exchange tube. The heat exchange tube has a first longitudinal side face and a second longitudinal side face opposite to and parallel to each other along the thickness direction of the heat exchange tube, and a third longitudinal side face and a fourth longitudinal side face opposite to each other along a width direction of the heat exchange tube. A distance between the first longitudinal side face and the second longitudinal side face is less than a distance between the third longitudinal side face and the fourth longitudinal side face. The heat exchange tube is divided into four portions with an equal width along the width direction of the heat exchange tube, and the four portions includes a first heat exchange tube portion, a second heat exchange tube portion, a third heat exchange tube portion and a fourth heat exchange tube portion distributed along a direction from an inlet side of an airflow to an outlet side of the airflow. Each heat exchange tube portion includes at least two flow channels, and the flow channel extends in a length direction of the heat exchange tube. The respective flow channels of the four portions are spaced apart along the width direction of the heat exchange tube. The heat exchange tube has a cross section defined in the thickness direction of the heat exchange tube and the width direction of the heat exchange tube, and the cross section includes a flow section. A total area of a flow section of the first heat exchange tube portion is A1, a total area of a flow section of the second heat exchange tube portion being A2, a total area of a flow section of the third heat exchange tube portion being A3, a total area of a flow section of the fourth heat exchange tube portion is A4. The total area A1 of the flow section of the first heat exchange tube portion is 1.05-1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion.

An air conditioning refrigeration system according to embodiments of the present disclosure includes a multi-channel heat exchanger, a second heat exchanger, a compressor and a throttle valve. One of a first header of the multi-channel heat exchanger and a first end of the second heat exchanger is connected to an inlet end of the compressor, and the other one of the first header of the multi-channel heat exchanger and the first end of the second heat exchanger is connected to an outlet end of the compressor. The throttle valve is connected between a second header of the multi-channel heat exchanger and a second end of the second heat exchanger. The multi-channel heat exchanger includes a plurality of heat exchange tubes spaced apart along a thickness direction of the heat exchange tube. The heat exchange tube has a first longitudinal side face and a second longitudinal side face opposite to and parallel to each other along the thickness direction of the heat exchange tube, and a third longitudinal side face and a fourth longitudinal side face opposite to each other along a width direction of the heat exchange tube. A distance between the first longitudinal side face and the second longitudinal side face is less than a distance between the third longitudinal side face and the fourth longitudinal side face. The heat exchange tube is divided into four portions with an equal width along the width direction of the heat exchange tube, and the four portions includes a first heat exchange tube portion, a second heat exchange tube portion, a third heat exchange tube portion and a fourth heat exchange tube portion distributed along a direction from an inlet side of an airflow to an outlet side of the airflow. Each heat exchange tube portion includes at least two flow channels, and the flow channel extends in a length direction of the heat exchange tube. The respective flow channels of the four portions are spaced apart along the width direction of the heat exchange tube. The heat exchange tube has a cross section defined in the thickness direction of the heat exchange tube and the width direction of the heat exchange tube, and the cross section includes a flow section. A total area of a flow section of the first heat exchange tube portion is A1, a total area of a flow section of the second heat exchange tube portion being A2, a total area of a flow section of the third heat exchange tube portion being A3, a total area of a flow section of the fourth heat exchange tube portion is A4. The total area A1 of the flow section of the first heat exchange tube portion is 1.05-1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion.

Additional aspects and advantages of the present disclosure will be given in part in the following description, become apparent in part from the following description, or be learned from the practice of the present disclosure.

BRIEF DESCRIPTION OF THE DRAWINGS

The above and/or additional aspects and advantages of the present disclosure will become apparent and easy to understand from following descriptions of embodiments in combination with accompanying drawings, in which:

FIG. 1 is a schematic view of a multi-channel heat exchanger according to an embodiment of the present disclosure;

FIG. 2 is a schematic side view of a multi-channel heat exchanger according to an embodiment of the present disclosure (an arrow direction is an air flow direction);

FIG. 3 is a schematic view of a fin of a multi-channel heat exchanger according to an embodiment of the present disclosure from a perspective;

FIG. 4 is a schematic view of a fin of a multi-channel heat exchanger according to an embodiment of the present disclosure from another perspective;

FIG. 5 is a schematic view of a fin of a multi-channel heat exchanger according to an embodiment of the present disclosure;

FIG. 6 is a schematic view of a fin of a multi-channel heat exchanger according to an embodiment of the present disclosure;

FIG. 7 is a sectional view of a heat exchange tube of a multi-channel heat exchanger according to an embodiment of the present disclosure;

FIG. 8 is a sectional view of a heat exchange tube of a multi-channel heat exchanger according to an embodiment of the present disclosure;

FIG. 9 is a sectional view of a heat exchange tube of a multi-channel heat exchanger according to an embodiment of the present disclosure;

FIG. 10 is a sectional view of a heat exchange tube of a multi-channel heat exchanger according to an embodiment of the present disclosure;

FIG. 11 is a sectional view of a heat exchange tube of a multi-channel heat exchanger according to an embodiment of the present disclosure;

FIG. 12 is a sectional view of a heat exchange tube of a multi-channel heat exchanger according to an embodiment of the present disclosure.

DETAILED DESCRIPTION

Embodiments of the present disclosure are described in detail below, and examples of the embodiments are shown in accompanying drawings. The same or similar elements or the elements having same or similar functions are denoted by the same or similar reference numerals throughout the descriptions. The following embodiments described with reference to the accompanying drawings are exemplary and are only intended to explain the present disclosure, rather than limit the present disclosure.

A multi-channel heat exchanger 100 according to embodiments of the present disclosure will be described below with reference to FIGS. 1 to 12.

As shown in FIG. 1 and FIG. 2, the multi-channel heat exchanger 100 according to the embodiments of the present disclosure includes a first header 10, a second header 20 and a plurality of heat exchange tubes 30.

As shown in FIG. 1, an axial direction of the first header 10 may be parallel to an axial direction of the second header 20, the first header 10 and the second header 20 may be arranged in parallel to each other and spaced apart from each other, and the first header 10 and the second header 20 are distributed along a length direction of the heat exchange tube 30. The first header 10 may be configured as an inlet header, and the second header 20 may be configured as an outlet header. Alternatively, the first header 10 may be configured as an outlet header, and the second header 20 may be configured as an inlet header.

As shown in FIG. 1, the plurality of heat exchange tubes 30 are spaced apart along a thickness direction of the heat exchange tube 30, the thickness direction of the heat exchange tube 30 may be parallel to the axial direction of the first header 10 and the axial direction of the second header 20, and the plurality of heat exchange tubes 30 may be spaced apart along the axial direction of the first header 10 and the axial direction of the second header 20. As shown in FIG. 2, a first end of the heat exchange tube 30 is connected to the first header 10, and a second end of the heat exchange tube 30 is connected to the second header 20, so as to communicate the first header 10 with the second header 20, so that a heat exchange medium may flow in an order of the first header 10, the heat exchange tube 30 and the second header 20 or in an order of the second header 20, the heat exchange tube 30 and the first header 10. The first header 10 may be provided with a first port, and the second header 20 may be provided with a second port. The first port and the second port are configured to be connected to an external pipeline, so as to connect the heat exchanger in a whole air conditioning system or other heat exchange systems.

As shown in FIGS. 7 to 12, the heat exchange tube 30 has a first longitudinal side face 30 a, a second longitudinal side face 30 b, a third longitudinal side face 30 c and a fourth longitudinal side face 30 d.

The first longitudinal side face 30 a and the second longitudinal side face 30 b are opposite to and parallel to each other along the thickness direction of the heat exchange tube 30, and the third longitudinal side face 30 c and the fourth longitudinal side face 30 d are opposite to each other along a width direction of the heat exchange tube 30. A distance between the first longitudinal side face 30 a and the second longitudinal side face 30 b is less than a distance between the third longitudinal side face 30 c and the fourth longitudinal side face 30 d, i.e., a thickness of the heat exchange tube 30 is less than a width of the heat exchange tube 30.

In a practical application of the multi-channel heat exchanger 100, an air flows through a gap between two heat exchange tubes 30, i.e., the air passes by the first longitudinal side face 30 a and the second longitudinal side face 30 b. In the heat exchange tube 30 of the present disclosure, the first longitudinal side face 30 a and the second longitudinal side face 30 b are arranged in parallel, i.e., the thickness of the heat exchange tube 30 is constant along an air input direction. Therefore, the heat exchange tube 30 itself has little effect on the fluidity of the air.

As shown in FIGS. 7 to 12, the heat exchange tube 30 is divided into four portions with an equal width along the width direction of the heat exchange tube 30. The four portions include a first heat exchange tube portion, a second heat exchange tube portion, a third heat exchange tube portion and a fourth heat exchange tube portion distributed along a direction from an inlet side of an airflow to an outlet side of the airflow. Each heat exchange tube portion includes at least two flow channels 30 e, and the flow channel 30 e extends in the length direction of the heat exchange tube. Moreover, the respective flow channels 30 e in the four heat exchange tube portions are spaced apart along the width direction of the heat exchange tube 30. The heat exchange tube 30 has a cross section defined in the thickness direction of the heat exchange tube 30 and the width direction of the heat exchange tube 30, and the cross section includes a flow section. A total area of a flow section of the first heat exchange tube portion is A1 and a total area of a flow section of the fourth heat exchange tube portion is A4. The total area A1 of the flow section of the first heat exchange tube portion is 1.05-1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion. A total area of a flow section of the second heat exchange tube portion is A2 and a total area of a flow section of the third heat exchange tube portion is A3. It should be noted that the heat exchange tube 30 of the present disclosure includes four portions divided equally along its width direction, and the distribution of the flow channels 30 e has no direct corresponding relationship with the division of the heat exchange tube. Therefore, at least part of the flow channel 30 e may be divided into a former heat exchange tube portion and a rest portion of the flow channel 30 e may be divided into a latter heat exchange tube portion in a specific division process. Therefore, the flow section of the heat exchange tube portion referred to in the present disclosure includes a cross section of the complete flow channel and a cross section of the incomplete flow channel located in the heat exchange tube portion.

Since the multi-channel heat exchanger 100 has a temperature difference on a windward side and a leeward side, when the total area A1 of the flow section of the first heat exchange tube portion is less than 1.05 times of the total area A4 of the flow section of the fourth heat exchange tube portion, the difference between the refrigerant in the flow channels of the first heat exchange tube portion and the refrigerant in the flow channels of the fourth heat exchange tube portion is small if the multi-channel heat exchanger 100 is used as an evaporator, which will result in that the refrigerant in the flow channels of the fourth heat exchange tube portion cannot have a sufficient heat exchange. For example, the liquid refrigerant in the flow channels at an outlet of the multi-channel heat exchanger 100 cannot be evaporated.

When the total area A1 of the flow section of the first heat exchange tube portion is greater than 1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion, the difference between the refrigerant in the flow channels of the first heat exchange tube portion and the refrigerant in the flow channels of the fourth heat exchange tube portion is large if the multi-channel heat exchanger 100 is used as the evaporator, which will result in that the refrigerant in the flow channels of the first heat exchange tube portion is evaporated too fully, thus causing a waste of space, and which will also have an impact on the structural safety of the multi-channel heat exchanger 100, thus causing a decrease of burst pressure.

Therefore, when the total area A1 of the flow section of the first heat exchange tube portion is 1.05-1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion, the design of the flow channels can meet the safety of the multi-channel heat exchanger 100 so as not to cause a waste of excess space, and also can make full use of the temperature difference between the windward side and the leeward side of the multi-channel heat exchanger 100, so as to allow the refrigerant in different flow channels to fully exchange heat, thus effectively reducing a temperature gradient on the cross section of the heat exchange tube of the multi-channel heat exchanger 100, balancing the temperature difference between the refrigerant in the heat exchange tube on the windward side and the refrigerant in the heat exchange tube on the leeward side, achieving the optimal balanced state of outlet overheating, and hence improving the heat exchange performance of the multi-channel heat exchanger 100.

Therefore, the total area A2 of the flow section of the second heat exchange tube portion may be 1.3 times of the total area A3 of the flow section of the third heat exchange tube portion, and the total area A3 of the flow section of the third heat exchange tube portion may be 1.2 times of the total area A4 of the flow section of the fourth heat exchange tube portion, i.e., flow sectional areas of the flow channels 30 e of the four heat exchange tube portions gradually decrease from the air inlet side to the air outlet side. Of course, the number of groups of the flow channels 30 e is not limited to four, but can also be more, such as six, seven or eight. Distances from any one of the flow channels 30 e in the four heat exchange tube portions to two flow channels 30 e adjacent to this flow channel 30 e can be set to be equal, so that each group of flow channels 30 e are evenly arranged.

In some embodiments of the present disclosure, distances from at least one of the flow channels 30 e in the four heat exchange tube portions to two flow channels 30 e adjacent to the at least one flow channel 30 e may be different.

It can be understood that in a process of the airflow flowing through the multi-channel heat exchanger 100, a temperature difference between the airflow on a windward side of the multi-channel heat exchanger 100 and the heat exchange medium is large, and a temperature difference between the airflow on a leeward side of the multi-channel heat exchanger 100 and the heat exchange medium is small. In this way, a heat exchange demand of the airflow on the leeward side of the multi-channel heat exchanger 100 is less than a heat exchange demand of the airflow on the windward side of the multi-channel heat exchanger 100. The windward side of the multi-channel heat exchanger 100 corresponds to the inlet side of the airflow and the leeward side of the multi-channel heat exchanger 100 corresponds to the outlet side of the airflow.

In the related art, the flow sectional areas of the plurality of flow channels 30 e of the multi-channel heat exchanger 100 from the windward side to the leeward side are the same. Due to the heat transfer between the airflow and the heat exchange medium, the temperatures of the heat exchange media in the respective flow channels 30 e arranged side by side along a wind direction (a transverse direction or the width direction of the heat exchange tube 30) are different. Therefore, the heat exchange medium in the flow channel adjacent to the windward side may have been evaporated or condensed, while the heat exchange medium in a latter flow channel (for example, the flow channel adjacent to the leeward side) along the transverse direction may have not been evaporated or condensed.

In some embodiments, a distance between any two adjacent flow channels 30 e in the first heat exchange tube portion is B1, and a distance between any two adjacent flow channels 30 e in the second heat exchange tube portion is B2. B1 is greater than or equal to B2, i.e., in multiple groups of flow channels 30 e, the distance between the flow channels in the respective groups of flow channels 30 e gradually decreases from the inlet side of the airflow to the outlet side of the airflow.

In some embodiments, in the respective flow channels 30 e of the first heat exchange tube portion, a sum of the flow sectional areas of the flow channels 30 e completely located in the first heat exchange tube portion is C1, and in the respective flow channels 30 e of the second heat exchange tube portion, a sum of the flow sectional areas of the flow channels 30 e completely located in the second heat exchange tube portion is C2. C2 is greater than or equal to C1. In other words, the flow sectional areas of the flow channels 30 e in the respective heat exchange tube portions gradually decrease from the inlet side of the airflow to the outlet side of the airflow. It should be noted that the heat exchange tube 30 of the present disclosure includes four portions divided equally along its width direction, and the distribution of the flow channels 30 e has no direct corresponding relationship with the division of the heat exchange tube. Therefore, at least part of the flow channel 30 e may be divided into a former heat exchange tube portion and a rest portion of the flow channel 30 e may be divided into a latter heat exchange tube portion in a specific division process.

In some embodiments of the present disclosure, a sum of the flow sectional areas of the respective flow channels of the first heat exchange tube portion is greater than or equal to a sum of the flow sectional areas of the respective flow channels of the second heat exchange tube portion.

In the present disclosure, as shown in FIGS. 7 to 12, the flow sectional areas of the corresponding flow channels 30 e in the plurality of heat exchange tube portions are configured to decrease sequentially from the air inlet side to the air outlet side, so that flow quantities of the heat exchange media in the plurality of heat exchange tube portions may be decreased sequentially from the air inlet side to the air outlet side, i.e., the heat exchange effect of the multi-channel heat exchanger 100 decreases gradually from the air inlet side to the air outlet side. Thus, the heat exchange amount on the windward side of the multi-channel heat exchanger 100 and the heat exchange amount on the leeward side of the multi-channel heat exchanger 100 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, respectively, so that the heat exchange effects on two sides of the multi-channel heat exchanger 100 can better meet the actual requirements, a temperature difference between the windward side and the leeward side of the multi-channel heat exchanger 100 is balanced, and a situation in which one side of the multi-channel heat exchanger 100 is overcooled and the other side of the multi-channel heat exchanger 100 is overheated is prevented, thus ensuring the reasonable and safe use of the multi-channel heat exchanger 100, and improving the heat exchange performance of the multi-channel heat exchanger 100.

In the heat exchange tube 30 according to the embodiments of the present disclosure, the flow sectional areas of the flow channels in the four heat exchange tube portions are configured to decrease sequentially from the air inlet side to the air outlet side, so that the heat exchange amount on the windward side of the multi-channel heat exchanger 100 and the heat exchange amount on the leeward side of the multi-channel heat exchanger 100 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, respectively, so as to effectively balance the temperature difference between the refrigerant in the heat exchange tube 30 on the windward side and the refrigerant in the heat exchange tube 30 on the leeward side, and to optimize the degree of outlet overcooling or overheating, thus improving the heat exchange performance of the multi-channel heat exchanger 100.

In some embodiments, as shown in FIG. 3, the multi-channel heat exchanger 100 further includes a fin 40. The fin 40 is arranged between two heat exchange tubes 30 along the thickness direction of the heat exchange tube 30, and the fin 40 is connected to the two heat exchange tubes 30, respectively. The fin includes first to nth groups of fins 40.

As shown in FIG. 4, each group includes at least one fin 40. The first to nth groups of fins 40 are all mounted between the first longitudinal side face 30 a of one heat exchange tube 30 and the second longitudinal side face 30 b of an adjacent heat exchange tube 30, and the first to nth groups of fins 40 are arranged sequentially along the width direction of the heat exchange tube 30. The first group of fins 40, . . . , the nth group of fins 40 are distributed along the direction from the air inlet side to the air outlet side, in which 1≤n, and n is an integer.

The heat exchange tube 30 is provided with the plurality of flow channels 30 e in the width direction, so that the plurality of flow channels 30 e may correspond to the n groups of fins 40. Therefore, the heat of the heat exchange medium in the multi-channel heat exchanger 100 may be diffused to the fin 40, so as to exchange heat with the airflow. Moreover, the fin 40 has a large surface area, so that the airflow can fully exchange heat with the fin 40. Thus, the heat dissipation effect of each portion of the multi-channel heat exchanger 100 can be maintained at a high level.

An air-side heat transfer coefficient of the nth group of fins 40 is less than an air-side heat transfer coefficient of the first group of fins 40. The air-side heat transfer coefficients of the n groups of fins 40 decrease sequentially from the first group of fins to the nth group of fins, and the heat transfer coefficient of the fin 40 adjacent to the air inlet side is greater than the heat transfer coefficient of the fin 40 adjacent to the air outlet side, so that the plurality of groups of fins 40 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, so as to effectively balance the temperature difference between the refrigerant in the heat exchange tube 30 on the windward side and the refrigerant in the heat exchange tube 30 on the leeward side, and to optimize the degree of outlet overcooling or overheating, thus improving the heat exchange performance of the multi-channel heat exchanger 100.

In some embodiments, the first to nth groups of fins 40 each include a plurality of louvers 40 a arranged along the width direction of the heat exchange tube 30. The number of the louvers 40 a of the first group of fins 40 is Q₁, . . . , the number of the louvers 40 a of a kth group of fins 40 is Q_(k), . . . , and the number of the louvers 40 a of the nth group of fins 40 is Q_(n), in which Q₁ is greater than Q_(n), and when n is greater than 1, Q_(k−1) is greater than Q_(k).

That is, as shown in FIG. 5, in the n groups of fins 40, the number of the louvers 40 a decreases sequentially from the first group to the nth group, and the more the number of the louvers 40 a, the better the heat exchange effect, so that the heat exchange effect of the multi-channel heat exchanger 100 on the air inlet side is greater than the heat exchange effect of the multi-channel heat exchanger 100 on the air outlet side. Therefore, the heat exchange effect of the multi-channel heat exchanger 100 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, thus optimizing the degree of outlet overcooling or overheating, avoiding the situation of overheating at one side and overcooling at the other side, and improving the rationality of the structural design of the multi-channel heat exchanger 100. In some embodiments, the multi-channel heat exchanger 100 has at least one of the following features.

a. As shown in FIG. 4 and FIG. 6, an opening width of the louver 40 a in the first group of fins 40 is W₁, . . . , an opening width of the louver 40 a in the kth group of fins 40 is W_(k), . . . , and an opening width of the louver 40 a in the nth group of fins 40 is W_(n), in which W₁ is greater than W_(n), and when n is greater than 1, W_(k−1) is greater than W_(k). Thus, in the n groups of fins 40, the opening width of the louver 40 a decreases sequentially from the first group to the nth group, and the larger the opening width of the louver 40 a, the better the heat exchange effect, so that the heat exchange effect of the multi-channel heat exchanger 100 on the air inlet side is greater than the heat exchange effect of the multi-channel heat exchanger 100 on the air outlet side. Therefore, the heat exchange effect of the multi-channel heat exchanger 100 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, and the heat exchange performance of the multi-channel heat exchanger 100 is improved.

b. As shown in FIG. 4, an opening angle of the louver 40 a in the first group of fins 40 is R₁, . . . , an opening angle of the louver 40 a in the kth group of fins 40 is R_(k), . . . , and an opening angle of the louver 40 a in the nth group of fins 40 is R_(n), in which R₁ is greater than R_(n), and when n is greater than 1, R_(k−1) is greater than R_(k). Therefore, in the n groups of fins, the opening angle of the louver 40 a decreases sequentially from the first group to the nth group, and the larger the opening angle of the louver 40 a, the better the heat exchange effect, so that the heat exchange effect of the multi-channel heat exchanger 100 on the air inlet side is greater than the heat exchange effect of the multi-channel heat exchanger 100 on the air outlet side. Therefore, the heat exchange effect of the multi-channel heat exchanger 100 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, and the heat exchange performance of the multi-channel heat exchanger 100 is improved.

c. As shown in FIG. 4, an opening length of the louver 40 a in the first group of fins 40 is L₁, . . . , an opening length of the louver 40 a in the kth group of fins 40 is L_(k), . . . , and an opening length of the louver 40 a in the nth group of fins 40 is L_(n), in which L₁ is greater than L_(n), and when n is greater than 1, L_(k−1) is greater than L_(k). Therefore, in the n groups of fins, the opening length of the louver 40 a decreases sequentially from the first group to the nth group, and the larger the opening length of the louver 40 a, the better the heat exchange effect, so that the heat exchange effect of the multi-channel heat exchanger 100 on the air inlet side is greater than the heat exchange effect of the multi-channel heat exchanger 100 on the air outlet side. Therefore, the heat exchange effect of the multi-channel heat exchanger 100 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, and the heat exchange performance of the multi-channel heat exchanger 100 is improved.

Therefore, when the multi-channel heat exchanger 100 of the present disclosure meets at least one of the above features, the air-side heat transfer coefficient or the heat dissipation performance of a former group of fins 40 is better than the air-side heat transfer coefficient of a latter group of fins 40. In cooperation with a former group of flow channels 30 e with a large flow sectional area, the heat exchange between the fin 40 on the windward side and the air can be further increased, and the heat exchange from the refrigerant to the air is increased, so that the heat exchange medium on the leeward side can also have an effective heat exchange when exchanging heat on the leeward side, so as to balance the heat exchange effects on the two sides of the multi-channel heat exchanger 100.

In some embodiments, as shown in FIG. 3, a spacing between two adjacent fins 40 in the first group of fins 40 along the length direction of the heat exchange tube 30 is F_(p) _(l) , . . . , a spacing between two adjacent fins 40 in the kth group of fins 40 along the length direction of the heat exchange tube 30 is F_(p) _(k) , . . . , and a spacing between two adjacent fins 40 in the nth group of fins 40 along the length direction of the heat exchange tube 30 is F_(p) _(n) , in which F_(p) _(l) , is less than F_(p) _(n) , and when n is greater than 1, F_(p) _(k) _(k−1), is less than F_(p) _(k) . In other words, the spacing between the two adjacent fins 40 in the former group of fins 40 is less than the spacing between the two adjacent fins 40 in the latter group of fins 40. Therefore, the air-side heat transfer coefficient or the heat dissipation performance of the former group of fins 40 is better than the air-side heat transfer coefficient of the latter group of fins 40. In cooperation with the former group of flow channels 30 e with the large flow sectional area, the heat exchange between the fin 40 on the windward side and the air can be further increased, and the heat exchange from the refrigerant to the air is increased, so that the heat exchange medium on the leeward side can also have an effective heat exchange when exchanging heat on the leeward side, so as to balance the heat exchange effects on the two sides of the multi-channel heat exchanger 100.

Therefore, relevant parameters of the flow sectional area of the flow channel 30 e in the heat exchange tube 30 and the fin 40 are designed cooperatively, so that a temperature gradient on the cross section of the heat exchange tube 30 of the multi-channel heat exchanger 100 can be effectively reduced, the temperature difference between the heat exchange medium on the windward side and the heat exchange medium on the leeward side can be balanced, and the degree of outlet overcooling or overheating can be optimized, thus improving the heat exchange performance of the multi-channel heat exchanger 100.

A boss may be arranged on the fin 40, and a ratio of the number of the bosses of the fin 40 on the windward side to the number of the bosses of the fin 40 on the leeward side may be increased. Alternatively, a ratio of a contact area of the boss of the fin 40 on the windward side to a contact area of the boss of the fin 40 on the leeward side may be increased. Alternatively, a flanging height of a portion of the fin 40 on the windward side may be reduced and the number of openings on the fin 40 may be increased from the windward side to the leeward side. A distribution density of the fins 40 may be adjusted, for example, the density of the fins 40 on the windward side is greater than the density of the fins 40 on the leeward side, so as to balance the heat exchange effects on the two sides of the multi-channel heat exchanger 100.

In some embodiments, as shown in FIG. 8 and FIG. 9, each heat exchange tube portion includes a plurality of flow channels 30 e, and the flow sectional area of each flow channel 30 e in the same heat exchange tube portion is the same, so that the plurality of flow channels 30 e in each heat exchange tube portion may allow the heat exchange medium to flow, thus increasing the overall heat exchange efficiency of the multi-channel heat exchanger 100.

In some embodiments, the multi-channel heat exchanger 100 has at least one of the following features.

a. As shown in FIG. 8 and FIG. 9, a shape of the cross section of each flow channel 30 e in the same heat exchange tube portion is the same, so as to facilitate the extrusion of the heat exchange tube 30.

b. As shown in FIG. 8 and FIG. 9, each heat exchange tube portion includes a plurality of flow channels 30 e, and the number of the flow channels 30 e in each heat exchange tube portion is the same, so as to make the overall structure of the multi-channel heat exchanger 100 more regular.

c. As shown in FIG. 8, sizes of any two flow channels 30 e along the width direction of the heat exchange tube 30 are the same, and sizes of the flow channels 30 e in different heat exchange tube portions along the thickness direction of the heat exchange tube 30 are different. However, the flow sectional areas of the flow channels 30 e in the plurality of heat exchange tube portions still decrease sequentially from the windward side to the leeward side.

d. As shown in FIG. 7 and FIG. 9, sizes of any two flow channels 30 e along the thickness direction of the heat exchange tube 30 are the same, and sizes of the flow channels 30 e in different heat exchange tube portions along the width direction of the heat exchange tube 30 are different. However, the flow sectional areas of the groups of flow channels 30 e still decrease sequentially from the windward side to the leeward side.

e. An outer profile of each flow channel 30 e is the same. For example, the outer profile of each flow channel 30 e may be one of a rectangle, a circle, a hexagon and a triangle. Moreover, at least part of the flow channels 30 e are provided with an inner rib 38, and the inner rib is mainly arranged in the flow channel 30 e adjacent to the leeward side, so as to reduce the flow sectional area of the flow channel 30 e on the leeward side.

In some embodiments, at least one of the flow channels 30 e in the second heat exchange tube portion has a flow sectional area greater than or equal to any one of the flow channels 30 e in the third heat exchange tube portion. At least two of the flow channels 30 e in the first heat exchange tube portion, the flow channels 30 e in the second heat exchange tube portion and the flow channels 30 e in the third heat exchange tube portion have the same flow sectional area. Moreover, the number of the flow channels 30 e in the first heat exchange tube portion, the number of the flow channels 30 e in the second heat exchange tube portion and the number of the flow channels 30 e in the third heat exchange tube portion are configured to be the same, or are configured to decrease sequentially.

In some embodiments, an outer shape of the cross section of the heat exchange tube 30 is circular, a plurality of inner ribs 38 are arranged in the heat exchange tube 30, and the number of the inner ribs 38 on the windward side is less than the number of the inner ribs 38 on the leeward side, so as to increase a flow resistance of the heat exchange medium on the leeward side and reduce a flow resistance of the heat exchange medium on the windward side. The plurality of inner ribs 38 extend radially outwards from a center of the heat exchange tube 30, and divide the cross section of the heat exchange tube 30 into a plurality of flow channels 30 e. Since the number of the inner ribs 38 on the windward side is less than the number of the inner ribs 38 on the leeward side, the number of the flow channels 30 e on the windward side is also less than the number of the flow channels 30 e on the leeward side.

As shown in FIG. 10, in some other embodiments, the inner rib 38 is arranged in a portion of the heat exchange tube 30 adjacent to the leeward side, and no inner rib 38 is arranged in a portion of the heat exchange tube 30 adjacent to the windward side. Alternatively, both the portions of the heat exchange tube 30 adjacent to the windward side and adjacent to the leeward side are provided with the inner rib 38, while more inner ribs 38 are arranged in the portion of the heat exchange tube 30 adjacent to the leeward side than in the portion of the heat exchange tube 30 adjacent to the windward side.

As shown in FIG. 10, the heat exchange tube 30 sequentially includes a flow channel 31 in a first heat exchange tube portion, a flow channel 32 in a second heat exchange tube portion, a flow channel 33 in a third heat exchange tube portion, a flow channel 34 in a fourth heat exchange tube portion, a flow channel 35 in a fifth heat exchange tube portion, a flow channel 36 in a sixth heat exchange tube portion, and a flow channel 37 in a seventh heat exchange tube portion, and the inner rib 38 is arranged in the flow channels 30 e in multiple heat exchange tube portions adjacent to the leeward side.

Alternatively, the outer shape of the cross section of the heat exchange tube 30 is configured to be oval or polygonal. As shown in FIGS. 7 to 12, the outer shape of the heat exchange tube 30 is oval, and the number of the flow channels 30 e or the area of the flow channel 30 e on the windward side is larger than the number of the flow channels 30 e or the area of the flow channel 30 e on the leeward side. Alternatively, the heat exchange tube 30 adopts a wire tube, and along a direction from the windward side to the leeward side, the number of the wire tubes on the windward side is larger than the number of the wire tubes on the leeward side, or an inner section of the wire tube on the windward side is greater than an inner section of the wire tube on the leeward side.

Therefore, through the shape of the heat exchange tube 30 as well as the shape and arrangement of the flow channels 30 e, the heat exchange amount on the windward side of the multi-channel heat exchanger 100 and the heat exchange amount on the leeward side of the multi-channel heat exchanger 100 can match with the actual heat exchange requirements, so as to effectively reduce the temperature gradient on the cross section of the heat exchange tube 30 of the multi-channel heat exchanger 100, balance the temperature difference between the heat exchange medium on the windward side and the heat exchange medium on the leeward side, and optimize the degree of outlet overcooling or overheating, thus improving the heat exchange performance of the multi-channel heat exchanger 100.

The present disclosure further provides an air conditioning refrigeration system.

The air conditioning refrigeration system according to embodiments of the present disclosure includes a multi-channel heat exchanger 100 according to any one of the above embodiments, a second heat exchanger, a compressor and a throttle valve. One of a first header 10 of the multi-channel heat exchanger 100 and a first end of the second heat exchanger is connected to an inlet end of the compressor, the other one of the first header 10 of the multi-channel heat exchanger 100 and the first end of the second heat exchanger is connected to an outlet end of the compressor, and the throttle valve is connected between a second header 20 of the multi-channel heat exchanger 100 and a second end of the second heat exchanger.

Therefore, the above multi-channel heat exchanger 100 is arranged in the air conditioning refrigeration system, so that the heat exchange medium in each heat exchange tube of the air conditioning refrigeration system can effectively exchange heat with the airflow, a local heat exchange will not have a lack or an excess, the rationality of the structural design of the air conditioning refrigeration system is improved and the practicability of the air conditioning refrigeration system is improved.

Reference throughout this specification to “an embodiment,” “some embodiments,” “an exemplary embodiment,” “an example,” “a specific example,” or “some examples,” means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present disclosure. Thus, the exemplary descriptions of the above terms throughout this specification are not necessarily referring to the same embodiment or example. Moreover the particular features, structures, materials or characteristic described may be combined in a suitable manner in any one or more embodiments or examples.

Although embodiments of the present disclosure have been shown and described, it would be appreciated by those skilled in the art that various changes, modifications, alternatives and variations may be made in the embodiments without departing from principles and purposes of the present disclosure. The scope of the present disclosure is defined by the claims and their equivalents. 

1. A multi-channel heat exchanger, comprising: a plurality of heat exchange tubes spaced apart along a thickness direction of the heat exchange tube, the heat exchange tube having a first longitudinal side face and a second longitudinal side face opposite to and parallel to each other along the thickness direction of the heat exchange tube, and a third longitudinal side face and a fourth longitudinal side face opposite to each other along a width direction of the heat exchange tube, a distance between the first longitudinal side face and the second longitudinal side face being less than a distance between the third longitudinal side face and the fourth longitudinal side face, the heat exchange tube being divided into four portions with an equal width along the width direction of the heat exchange tube, the four portions comprising a first heat exchange tube portion, a second heat exchange tube portion, a third heat exchange tube portion and a fourth heat exchange tube portion distributed along a direction from an inlet side of an airflow to an outlet side of the airflow, each heat exchange tube portion comprising at least two flow channels, the flow channel extending in a length direction of the heat exchange tube, the respective flow channels of the four portions being spaced apart along the width direction of the heat exchange tube, the heat exchange tube having a cross section defined in the thickness direction of the heat exchange tube and the width direction of the heat exchange tube, the cross section comprising a flow section, a total area of a flow section of the first heat exchange tube portion being A1, a total area of a flow section of the second heat exchange tube portion being A2, a total area of a flow section of the third heat exchange tube portion being A3, a total area of a flow section of the fourth heat exchange tube portion being A4, and the total area A1 of the flow section of the first heat exchange tube portion being 1.05-1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion.
 2. The multi-channel heat exchanger according to claim 1, wherein distances from at least one of the flow channels in the four heat exchange tube portions to two flow channels adjacent to the at least one of the flow channels are different.
 3. The multi-channel heat exchanger according to claim 1, wherein a distance between any two adjacent flow channels in the first heat exchange tube portion is greater than or equal to a distance between any two adjacent flow channels in the second heat exchange tube portion.
 4. The multi-channel heat exchanger according to claim 1, wherein a sum of flow sectional areas of the flow channels completely located in the first heat exchange tube portion in the respective flow channels of the first heat exchange tube portion is greater than or equal to a sum of flow sectional areas of the flow channels completely located in the second heat exchange tube portion in the respective flow channels of the second heat exchange tube portion.
 5. The multi-channel heat exchanger according to claim 1, further comprising a fin, the fin being arranged between two heat exchange tubes along the thickness direction of the heat exchange tube and connected to the two heat exchange tubes, respectively, the fin comprising first to nth groups of fins, the first to groups of fins being distributed along the direction from the inlet side of the airflow to the outlet side of the airflow, wherein 1≤n, n is an integer, and an air-side heat transfer coefficient of the nth group of fins is less than an air-side heat transfer coefficient of the first group of fins.
 6. The multi-channel heat exchanger according to claim 5, wherein the first to nth groups of fins comprise a plurality of louvers arranged along the width direction of the heat exchange tube, and the number of the louvers of the first group of fins is greater than the number of the louvers of the nth group of fins.
 7. The multi-channel heat exchanger according to claim 6, wherein the multi-channel heat exchanger comprises at least one of following features: a. an opening width of the louver of the first group of fins is greater than an opening width of the louver of the nth group of fins; b. an opening angle of the louver of the first group of fins is greater than an opening angle of the louver of the nth group of fins; and c. an opening length of the louver of the first group of fins is greater than an opening length of the louver of the nth group of fins.
 8. The multi-channel heat exchanger according to claim 6, wherein a spacing between two adjacent fins in the first group of fins along the length direction of the heat exchange tube is less than a spacing between two adjacent fins in the nth group of fins along the length direction of the heat exchange tube.
 9. The multi-channel heat exchanger according to claim 1, wherein a flow sectional area of each flow channel in each the same heat exchange tube portion is the same.
 10. The multi-channel heat exchanger according to claim 9, wherein the multi-channel heat exchanger comprises at least one of following features: a. a shape of a cross sectional of each flow channel in the same heat exchange tube portion is the same; b. each heat exchange tube portion comprises a same number of flow channels; c. sizes of any two flow channels along the width direction of the heat exchange tube are the same, and sizes of the flow channels in different heat exchange tube portions along the thickness direction of the heat exchange tube are different; d. sizes of any two flow channels along the thickness direction of the heat exchange tube are the same, and sizes of the flow channels in different heat exchange tube portions along the width direction of the heat exchange tube are different; and e. at least part of the flow channels are provided with an inner rib.
 11. An air conditioning refrigeration system, comprising a multi-channel heat exchanger, a second heat exchanger, a compressor and a throttle valve, one of a first header of the multi-channel heat exchanger and a first end of the second heat exchanger being connected to an inlet end of the compressor, the other one of the first header of the multi-channel heat exchanger and the first end of the second heat exchanger being connected to an outlet end of the compressor, and the throttle valve being connected between a second header of the multi-channel heat exchanger and a second end of the second heat exchanger, the multi-channel heat exchanger, comprising a plurality of heat exchange tubes spaced apart along a thickness direction of the heat exchange tube, the heat exchange tube having a first longitudinal side face and a second longitudinal side face opposite to and parallel to each other along the thickness direction of the heat exchange tube, and a third longitudinal side face and a fourth longitudinal side face opposite to each other along a width direction of the heat exchange tube, a distance between the first longitudinal side face and the second longitudinal side face being less than a distance between the third longitudinal side face and the fourth longitudinal side face, the heat exchange tube being divided into four portions with an equal width along the width direction of the heat exchange tube, the four portions comprising a first heat exchange tube portion, a second heat exchange tube portion, a third heat exchange tube portion and a fourth heat exchange tube portion distributed along a direction from an inlet side of an airflow to an outlet side of the airflow, each heat exchange tube portion comprising at least two flow channels, the flow channel extending in a length direction of the heat exchange tube, the respective flow channels of the four portions being spaced apart along the width direction of the heat exchange tube, the heat exchange tube having a cross section defined in the thickness direction of the heat exchange tube and the width direction of the heat exchange tube, the cross section comprising a flow section, a total area of a flow section of the first heat exchange tube portion being A1, a total area of a flow section of the second heat exchange tube portion being A2, a total area of a flow section of the third heat exchange tube portion being A3, a total area of a flow section of the fourth heat exchange tube portion being A4, and the total area A1 of the flow section of the first heat exchange tube portion being 1.05-1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion.
 12. The air conditioning refrigeration system according to claim 11, wherein distances from at least one of the flow channels in the four heat exchange tube portions to two flow channels adjacent to the at least one of the flow channels are different.
 13. The air conditioning refrigeration system according to claim 11, wherein a distance between any two adjacent flow channels in the first heat exchange tube portion is greater than or equal to a distance between any two adjacent flow channels in the second heat exchange tube portion.
 14. The air conditioning refrigeration system according to claim 11, wherein a sum of flow sectional areas of the flow channels completely located in the first heat exchange tube portion in the respective flow channels of the first heat exchange tube portion is greater than or equal to a sum of flow sectional areas of the flow channels completely located in the second heat exchange tube portion in the respective flow channels of the second heat exchange tube portion.
 15. The air conditioning refrigeration system according to claim 11, wherein the multi-channel heat exchanger further comprises a fin, the fin is arranged between two heat exchange tubes along the thickness direction of the heat exchange tube and connected to the two heat exchange tubes, respectively, the fin comprises first to nth groups of fins, the first to nth groups of fins are distributed along the direction from the inlet side of the airflow to the outlet side of the airflow, wherein 1≤n, n is an integer, and an air-side heat transfer coefficient of the nth group of fins is less than an air-side heat transfer coefficient of the first group of fins.
 16. The air conditioning refrigeration system according to claim 15, wherein the first to nth groups of fins comprise a plurality of louvers arranged along the width direction of the heat exchange tube, and the number of the louvers of the first group of fins is greater than the number of the louvers of the nth group of fins.
 17. The air conditioning refrigeration system according to claim 16, wherein the multi-channel heat exchanger comprises at least one of following features: a. an opening width of the louver of the first group of fins is greater than an opening width of the louver of the nth group of fins; b. an opening angle of the louver of the first group of fins is greater than an opening angle of the louver of the nth group of fins; and c. an opening length of the louver of the first group of fins is greater than an opening length of the louver of the nth group of fins.
 18. The air conditioning refrigeration system according to claim 16, wherein a spacing between two adjacent fins in the first group of fins along the length direction of the heat exchange tube is less than a spacing between two adjacent fins in the nth group of fins along the length direction of the heat exchange tube.
 19. The air conditioning refrigeration system according to claim 11, wherein a flow sectional area of each flow channel in the same heat exchange tube portion is the same.
 20. The air conditioning refrigeration system according to claim 19, wherein the multi-channel heat exchanger comprises at least one of following features: a. a shape of a cross section of each flow channel in the same heat exchange tube portion is the same; b. each heat exchange tube portion comprises a same number of flow channels; c. sizes of any two flow channels along the width direction of the heat exchange tube are the same, and sizes of the flow channels in different heat exchange tube portions along the thickness direction of the heat exchange tube are different; d. sizes of any two flow channels along the thickness direction of the heat exchange tube are the same, and sizes of the flow channels in different heat exchange tube portions along the width direction of the heat exchange tube are different; and e. at least part of the flow channels are provided with an inner rib. 